Control of gear ratio changes in automatic transmission

Abstract: A system and method for controlling gear ratio changes in an automatic transmission includes an electronic microprocessor (50), an electronic memory (62) accessible to the microprocessor, solenoid-operated shift valves (70, 72, 74), pressure actuated friction clutches and brakes, a variable force solenoid-operated valve, a torque converter bypass friction clutch (82), and control algorithms that produce output signals to control the state of the solenoid-operated valves (70, 72, 74). The vehicle speed and engine speed at which upshifts and downshifts occur, according to a standard gear shift schedule, is compensated for loss of engine torque at conditions that differ from the conditions at which a reference shift schedule is defined. Vehicle speed is compensated for torque variation with reference to the ratio of current calculated engine torque divided by current engine output torque.

Description: This invention relates to control of gear ratio changes in automatic transmissions. More particularly, the invention pertains to altering, on the basis of variations in engine output torque, vehicle speed and engine speed, where upshifts, downshifts and torque converter bypass clutch engagements and releases are scheduled to occur according to reference schedules of control. Conventionally, the electronic control system for an automatic transmission is provided with a gear shift schedule that defines conditions of current engine throttle position and vehicle speed at which each gear ratio change is to occur. Generally, data located in look-up tables stored in electronic memory, relating vehicle speed and engine throttle position for each of the gear ratio changes, are used to produce a signal representing the desired gear ratio. When the desired gear ratio is different from the current gear ratio, a command signal is produced by the control to cause a change in state of solenoid-operated shift valves. This changes the state of the planetary gear units and causes the gear ratio to change. A reference schedule of gear shift boundaries is continually referenced during execution of control algorithms and used to produce an upshift signal and a downshift signal when a boundary of the gear shift schedule is crossed. Gear shifts are made by continually probing computing memory with current values of throttle position and vehicle speed, and determining, on the basis of the stored shift schedules, whether an upshift or downshift is required. Upshift points are determined also on the basis of maximum engine speed when a wide-open throttle condition is detected. U.S. Patent 4,943,921 describes an electronic control for scheduling gear shifts in an automatic transmission on the basis of variations in ambient barometric pressure. Various functions relating vehicle speed and throttle position determine the occurrence of each upshift and downshift by probing computer memory, in which the gearshift functions reside, with current values of the throttle position and vehicle speed. A reference gear shift schedule is corrected for the difference between the operating barometric pressure and a reference barometric pressure, at which the gear shift schedules are calibrated, to automatically compensate for the effect of barometric pressure variations on the gear shift schedule. US patent No. 4,393,463 describes an electronic control system in which a reference gear shift schedule defining conditions under which upshifts or downshifts in gear ratio from a current gear ratio can occur is selected from a set of predetermined schedules each corresponding to an inclination of the slope on which the vehicle is running, as detected by the vehicle traction, speed and acceleration, and control is effected by direct comparison of the vehicle speed with the selected shift schedule. It also describes a lockup control system for a bypass clutch operation on the basis of a fixed reference schedule. The present invention provides a method and system for controlling gear ratio changes in an automatic transmission as set forth in claims 1 and 11 respectively. Further features of the invention are set forth in the subclaims. The method, according to this invention, for controlling gear ratio changes in an automatic transmission essentially alters vehicle speed and engine speed at which gear ratio changes are to occur, and the vehicle speed at which torque converter bypass locks/unlocks are to occur. The control compensates for changes in engine output torque from the engine torque at which reference gear shift schedules and a reference torque converter lock/unlock schedule are defined. The method involves developing a first gear shift schedule at which acceptable gear ratio changes are to occur, the schedule being developed at reference magnitudes of engine output torque BTR BASE. The function for determining the magnitude of BTR BASE with reference to the current engine speed and throttle is stored in electronic memory accessible to a microprocessor. Current engine output torque TQ NET is calculated continually as is the ratio TQ NORM defined as TQ NET/BTR BASE. A vehicle equipped with an internal combustion engine controlled by a throttle is calibrated to determine a torque interpolation factor TQ INTR, engine speed adjustment and vehicle speed adjustment values that are combined arithmetically to modify the engine speed and vehicle speed of the reference gear schedule. The torque interpolation factor, defined as a function with reference to the range of engine throttle position, is accessible continually for use in producing control outputs. Also stored in electronic memory are vehicle speed and engine speed adjustment values stored on the basis of engine throttle and the relevant upshift and downshift. A term comprising the product of the torque interpolation factor multiplied by the vehicle speed adjustment or engine speed adjustment is added algebraically to the corresponding engine speed or vehicle speed defined by the reference gear shift schedule. The resulting engine speed and vehicle speed compensates for a change of engine output torque from the torque at which the reference gear shift schedule is defined so that a desirable upshift or downshift occurs under current conditions without redefining an entirely new gear shift schedule. A torque converter bypass clutch is controlled by the method of the present invention by defining a vehicle speed adjustment value over the range of engine throttle positions. When the speed adjustment is multiplied by the current torque interpolation factor and that product is added to a vehicle speed from the reference schedule that defines when the bypass clutch is locked and unlocked, the result is a vehicle speed at which a desirable gear shift change occurs by compensating for engine output torque variations from the engine torque present when the reference bypass clutch lock/unlock schedule is defined. The invention will now be described further, by way of example, with reference to the accompanying drawings, in which: Figure 1 is a block diagram showing the relationship of an internal combustion engine, transmission, and electronic control module used. Figure 2 is a graph showing a reference schedule of upshifts and downshifts for a four-speed automatic transmission. Figure 3 is a schematic diagram of a microprocessor, an electronic memory, various input signals produced by sensors representing the current state of various operating parameters, and output signals used to control the components of an automatic transmission. Figure 4 shows a torque converter, bypass clutch, solenoid, and hydraulic valves for controlling the bypass clutch. Figure 5 is a graph showing a schedule that defines, in terms of vehicle speed and throttle position, the state of engagement and disengagement of a torque converter bypass clutch. Figure 6 is a graph showing the relation of torque interpolation factor and normalised engine output torque. Figure 7 is a table representing electronically stored value of expected torque output produced by an internal combustion engine when operating at current engine speed and throttle position. Figure 8 is a diagram of logic for controlling gear ratio shifting of an automatic transmission. Figure 9 is a table showing representative values of vehicle speed adjustment for upshifts and downshifts over a range of throttle positions. Figure 10 is a table showing representative values at wide-open throttle of engine speed adjustment for engine output torque. Figure 11 is a diagram of logic for controlling torque converter bypass clutch operation. Figure 12 is a graph of a function relating throttle position and vehicle speed adjustment of converter bypass clutch lockup for a particular gear ratio. Referring to Figure 1, air and fuel are inducted by an internal combustion engine 10, which drives a shaft connecting the engine output and transmission input having the speed of the engine, NE, and the engine brake torque TQ NET. Both the engine and transmission 11 are coupled to an electronic engine control module, which includes a microprocessor, input conditioning circuit, an electronic memory containing various algorithms for processing spark timing input, exhaust gas recirculation rate input, percent methonal fuel input, air/fuel ratio input, engine RPM input, engine air charge input, engine coolant temperature, firing cylinder indication input, engine operating hours, power steering pressure, timer input, air conditioning head pressure or air change temperature input, and a flag indicating whether the air conditioning compressor is on or off. These engine operating parameters and other such parameters and a method for determining engine brake torque TQ NET are described in U.S. Patent No. 5,241,855. The magnitude of engine brake torque is stored in computer memory as the variable TQ NET and engine speed as NE. Figure 2 shows gear ratio boundaries defined in terms of vehicle speed VS and throttle position TP REL. Throttle position corresponds to a signal produced by a throttle position sensor PRNDE indicating the amount of engine throttle displacement from a closed throttle or idle setting. Figure 2 shows where gear ratio changes, both upshifts and downshifts, are scheduled to occur automatically among the forward gear ratios produced by the transmission. Large values of TP REL occur near wide open throttle WOT, smaller values of TP REL indicate part throttle PT, and values near zero occur at nearly closed throttle positions CT. The data of Figure 2 are stored in read-only-memory ROM in the form of a look-up table. The lines marked FNXXS define boundaries where upshifts and downshifts occur according to the reference schedule of Figure 2, where XX represents the gear ratio change. At the right-hand end of the throttle position range near WOT, upshifts occur when engine speed has the values NEXXS. A signal indicating each commanded gear ratio GR CM is produced, according to the schedule of Figure 2, by a microprocessor using TP and VS as input. That signal causes a change in the state of solenoid-operated valves and a change of gear ratio to the commanded gear ratio. As VS and TP REL change during vehicle operation in a particular gear ratio such that a line of Figure 2 is crossed during a background pass, during which engine and transmission control algorithms are executed, from an operating condition defined by these variables during the previous background pass, need for a gear shift is indicated by changing GM CM following a comparison of the desired gear ratio from Figure 2 and the current gear ratio. For example, if the current operating condition passes from below the FN12S line to above that line, a gear shift from first gear to second gear is commanded because of the inequality between the current gear ratio (first gear) and the desired gear ratio from the schedule (second gear), provided other criteria considered by the control so permit. Similarly, downshifts may be commanded when the current operating condition passes through a downshift line, the dash lines of Figure 2. When the operating condition during the current background pass is located in the zone between adjacent upshift and downshift lines, no gear shift is commanded. Gear shifts are made also on the basis of engine speed corresponding to a WOT condition above which an upshift is commanded regardless of the TP value. As Figure 2 indicates, a 1-2 upshift occurs at engine speed NE12S, provided TP is equal to or greater than a predetermined wide open throttle TP. Each of the other upshift lines, 2-3 and 3-4, has a corresponding WOT shift point NE23S and NE34S. The WOT shift points are executed before shift points defined by the VS-TP relationship, as discussed below. Calibration constants are stored in ROM, accessible to the microprocessor, solely by reference to their memory addresses. Data stored in ROM or other electronic memory in the form of values of a first variable X, each X value having a single corresponding value of the second variable Y, recalled from memory by reference to a memory location and the first variable, are f(x) or "fox" functions. Data stored in ROM or other electronic memory in the form of multiple first variables X and Y, each combination thereof having a corresponding third variable Z, whose value is recalled from memory by reference to a memory location and variables X and Y, called "tables". Data recalled from tables and fox functions are automatically interpolated to correspond to the values of the variables used to recall the data. A "register" is a variable whose value is calculated through execution of control algorithms. The microprocessor 50 shown in Figure 3 is an integrated, central processor supplied with signals representing engine throttle position, engine speed, engine coolant temperature, torque converter speed, vehicle speed, a selected range of a gear selector, throttle valve pressure, the state of the selected transmission operating modes 52, the state of a brake switch 54, other input information mentioned above with reference to U.S. Patent No. 5 241 855, and signals representing the state of other operating parameters. Information conveyed by these input signals is conditioned by input conditioning circuitry 56 and transmitted on data bus 58 to a central processing unit 60 accessible to electronic memory 62. The electronic memory contains control algorithms for use in controlling gear shift scheduling, electronic pressure control EPC, and torque converter bypass clutch 82 operation. The central processing unit recalls information and control algorithms from electronic memory 62, executes the algorithms, and produces output signals carried on data bus 64 to output driver circuits 66, which produce electronic signals from the signals produced by the microprocessor. The output signals drive electrical solenoid-operated valves 70, 72, 74, 76, 78 located in an hydraulic valve body 68 adapted to respond to the output signals. The results of logical and arithmetic computations executed by the processor are stored in RAM, which is addressed, erased, rewritten, or changed in accordance with logic of the control algorithms. Data that are stored in memory include shift schedule information look-up tables, in which two variables, such as throttle position and vehicle speed, are mutually related and stored by reference to a particular gear ratio. Data stored in memory also includes functions, in which a first variable is used to select from memory corresponding variables and constants. The algorithms that control operation of the transmission are divided into several control modules executed sequentially in a known fashion during a background pass. The algorithms of each module are executed sequentially just as the modules themselves are executed sequentially. Information that results from the sensor input data and information stored in memory and learned from previous executions of background passes is used during execution of the control algorithms to produce electronic signals present at the output ports of the processor. Output signals drive on/off solenoid-operated shift valves 70, 72, 74, a variable force EPC solenoid 76, and a torque converter bypass clutch solenoid 78. Friction elements, such as clutches 80, 82, brakes, and servos, are pressurised and vented through operation of solenoid-operated shift valves 70, 72, 74. The state of solenoids 70, 72, 74 change when a gear ratio change is commanded as a result of executing control algorithms, and the friction elements are engaged and released in accordance with the state of those solenoids. Referring now to Figure 4, the lock-up clutch 82 of a torque converter 84 is alternately hard-locked or soft-locked (modulated) by directing hydraulic fluid through converter bypass-clutch control valve 86, which is supplied with regulated line pressure in line 88. A variable pressure valve 92 is supplied with constant pressure through line 94 from a solenoid-pressure regulator valve and is controlled by a pulse-width-modulated (PWM) signal applied to solenoid 78 from the microprocessor output. Valve 86 produces a pressure difference across bypass clutch 82. When clutch 82 is hard-locked, a direct mechanical connection between impeller 96 and turbine 98 is produced. The impeller of torque converter 84 is driven from the crankshaft 100 of an engine, and turbine 98 drives a transmission input shaft 102. When clutch 82 is disengaged, the turbine is driven hydrodynamically by the impeller. Figure 5 represents data from a look-up table stored in electronic memory relating vehicle speed and engine throttle position, each such table corresponding to a particular gear ratio. Line 110 represents the upper range of vehicle speed below which the torque converter 84 is unlocked by unlocking lockup clutch 82. For second gear ratio, line 110 carries the symbol FN2US. Line 112 defines the lower limit of vehicle speed over the range of engine throttle position, above which bypass clutch 82 is modulated or locked while the transmission is operating in the normal mode. For the second gear ratio, line 112 is represented symbolically by FN2LS. When the vehicle is operating in the range between curves 110 and 112, there is no change of the state of the bypass clutch 82. This range represents a hysteresis zone in which the current state of bypass clutch 82 is maintained. Also stored in electronic memory is a table of expected engine torque output corresponding to the current engine speed NE and throttle position TP REL. This table is identified as BTR BASE in Figure 7. The table is populated with engine torque values BTR BASE at which the reference shift schedule of Figure 2 is established. The nominal conditions, such as a 20° spark angle, and the engine torque output corresponding to those conditions, are the conditions and torque values at which the reference gear shift schedule, the schedule of Figure 2, is established. The variable normalised torque output of the engine TQ NORM is defined as the ratio of TQ NET/BTR BASE. This normalised torque is the basis for changes to the standard shift schedule of Figure 2 that are made to compensate for variations in the expected torque output of the engine. The function shown in Figure 6, relating TQ INTR and TQ NORM, is also stored in electronic memory in the form of a look-up table. The value of TQ INTR is substantially zero in a range of TQ NORM that straddles the value 1.0, rises above zero as TQ NORM increases above 1.0, and declines below zero when TQ NORM falls below the mid-range of TQ NORM values. The function relating TQ INTR and TQ NORM is determined by calibrating a vehicle equipped with an engine and automatic transmission such that desirable gear ratio changes are produced by altering the gear shift schedule of Figure 2 to compensate for changes in engine output torque. For example, TQ INTR may equal 0.0 in the mid-range of TQ NORM values, i.e., in a narrow band on either side of 1.0. The function of Figure 6 is determined with the value of vehicle speed adjustment, engine speed adjustment, and converter bypass clutch vehicle speed adjustment, discussed below with reference to Figures 9, 10, and 12. The control logic for scheduling gear ratio changes by controlling the states of shift solenoids 70, 72, 74 is described next with reference to Figure 8. The value of TQ NET is determined according to the method described in U.S. Patent No. 5 241 855. To determine the torque interpolation factor TQ INTR, BTR BASE is determined from the look-up table (Figure 7) entered with engine speed NE and throttle position TP REL. If the base torque value from this table is zero, TQ NORM is set equal to 1.0; otherwise, TQ NORM is equal to TQ NET/BTR BASE. In either case, TQ INTR is equal to the value determined from the function of Figure 6 when the table is referenced with values of TQ NORM. Turning now to Figure 8, the control algorithms for producing upshifts and downshifts in accordance with the present invention, by producing changes in the states of the solenoid-actuated shift valves 70, 72, 74, execute logic in the following order: first, a check is made to determine whether an upshift on the basis of engine speed is required; second, a check is made to determine whether an upshift based on vehicle speed is required; and third, a check is made to determine whether a downshift based on vehicle speed is required. At statement 120, the current commanded gear GR CM is compared to 1.0 in order to determine whether the first speed ratio is the desired speed ratio. If statement 120 is true, statement 122 is executed to determine whether filtered engine speed NE BART is greater than [NE12S + (TQ INTR * NE12TQ)], the sum of the engine speed of which an upshift from first gear to second gear would occur according to the reference gear shift schedule of Figure 2 and TQ INTR * NE12TQ. The constant NE12TQ is the engine speed adjustment value that compensates for engine output torque loss due to operation of the vehicle at conditions that differ from the conditions at which the reference gear shift schedule is determined. Engine speed is passed through a low pass filter implemented in software to reject high frequency speeds signals or noise. If statement 122 is true, at statement 124, the state of the solenoid-operated shift valves is changed to the combination of states required to produce the second forward speed ratio. The term TQ INTR * NE12TQ corrects, compensates, or adjusts for variations in engine output torque from the torque at which the schedule of Figure 2 is determined. The term NE12TQ is a calibrated differential engine speed, for example, -300 rpm, such that when it is multiplied by TQ INTR and added to the engine speed of the reference shift schedule, the sum is lower than the reference schedule engine speed. Therefore, the shift occurs at a lower engine speed and compensates for a change of engine torque from the engine torque at which the reference shift schedule is established. This action produces a more desirable gear ratio change than would the reference schedule at the lower engine output torque. If, for example, NE12S is 4000 rpm, TQ INTR is 1.0, and NE12TQ is -300 rpm, an upshift from first gear to second gear occurs at 3700 rpm instead of 4000 rpm. This reduction in engine speed accounts for a reduction in engine torque output due to a change in one of the engine operating parameters such as a change in the spark angle or air/fuel ratio at which the reference gear shift schedule is established. The values of TQ INTR and NE12TQ are determined by calibration, e.g., by operating the vehicle at a much higher elevation above sea level than the altitude at which the reference gear shift schedule was established, to determine the combination that will produce acceptable upshifts. If statement 122 is false, control passes to statement 126 where an inquiry, similar to that of statement 120, is made to determine whether the commanded gear is currently the second gear. If so, a check is made at statement 128 to determine whether engine speed exceeds NE23S + [TQ INTR*NE23TQ] where NE23S is the engine speed at which an upshift from the second gear ratio to the third gear ratio is scheduled to occur according to the reference shift schedule of Figure 2, and NE23TQ is a calibrated differential engine speed such that when it is multiplied by TQ INTR, the product of those terms corrects NE23S such that an acceptable upshift is made from the second gear to the third gear ratio. If statement 128 is true, control passes to 130 where the state of the shift valves is changed to the conditions at which the third gear ratio is produced. If statement 128 is false, control passes to 132 to determine whether the current commanded gear is equal to or less than the third gear ratio. If so, a check is made at 134, similar to those of statements 122 and 128, to determine whether engine speed is sufficiently high to produce an acceptable upshift to the fourth gear ratio by compensating for engine torque variations from the conditions at which the standard gear shift schedule is established. If 134 is true, at 136, the state of the gear shift lever, represented by the PRNDL signal, is checked to determine whether it is equal to 4, the position that would permit the fourth gear ratio to be produced. If so, at 138, the state of the solenoid actuated shift valves is changed to the combination of states that produce the fourth gear ratio. If any of statements 132, 134, or 136 is false, control passes to 140 in order to determine whether the commanded gear ratio is lower than the fourth speed ratio. If 140 is true, at 142, a check is made to see if vehicle speed VS is greater than FN34S + [TQ INTR * FN34TQ]. FN34S is the vehicle speed from Figure 2 where upshifts from the third speed ratio to the fourth speed ratio are scheduled to occur, and FN34TQ is a calibrated differential vehicle speed such that when it is multiplied by TQ INTR, the product of those terms corrects FN34S such that an acceptable upshift is made from the third gear to the fourth gear ratio. If 142 is true, at 144, the current state of the gear shift lever is compared to the fourth position. If statement 144 is true, control passes to 146 to determine whether the current PRNDL position has been changed from the PRNDL position recorded during the last executed background pass. If so, the state of the solenoid-operated shift valves is changed at 148 to produce an upshift of the fourth speed ratio. If any of the statements 142, 144, or 146 is false, control passes to 150 where it is determined whether the current commanded gear is less than the third gear ratio. If so, at 152, vehicle speed is compared to FN23S + (TQ INTR*FN23TQ) where FN23S is the vehicle speed at which a 2-3 upshift is scheduled to occur according to the schedule of Figure 2, and FN23TQ is the vehicle speed adjustment for a 2-3 upshift accounting for engine output torque loss. If 152 is true, at 154, the position of the PRNDL indicator is compared to 3. If 154 is equal to the third position, at 156, a check is made to see if the PRNDL position has changed from the last executed background pass. If both 154 and 156 are true, the state of the shift valves is changed at 158 to produce an upshift from the second gear ratio to the third gear ratio. If either of the statements 150, 152, or 156 is false, control passes to 160 to determine if the current commanded gear ratio is less than 2. If that statement is true, at 162, a check is made to see if vehicle speed is greater than FN12S + (TQ INTR*FN12TQ) where FN12S is the vehicle speed at which a 1-2 upshift occurs according to the schedule of Figure 2, and FN12TQ is the vehicle speed adjustment for a 1-2 upshift compensating for engine output torque loss. If the current vehicle speed exceeds the calculated value, at 164, the state of the shift valves is changed to produce the second gear ratio. If statement 160 or 162 is false, control passes to 166 to determine whether the current commanded gear is greater than the first gear ratio. If so, at 168, a check is made to determine whether vehicle speed is less than the vehicle speed at which a 2-1 downshift would occur according to the schedule of Figure 2 when compensated for torque reduction according to the equations discussed above. If statement 168 is true, at 170, the state of the shift valves is changed to produce a 2-1 downshift. Similarly, in statements 172, 174, and 176, a 3-2 downshift is produced by altering the state of the shift valves if the current vehicle speed is less than the engine torque compensated vehicle speed. If the commanded gear is greater than the third speed ratio, and the vehicle speed is less than the engine torque output compensated vehicle speed at which a 4-3 downshift is to occur, then at statement 182 the state of the shift valves is changed to produce the third speed ratio. If statement 180 is false, and the PRNDL position is equal to three, then a 4-3 downshift is initiated. Otherwise, if either of statements 178 or 184 is false, control exits the gear shift control algorithm at 186. Figures 9 and 10 show representatives of values of FNXXTQ and NEXXTQ, respectively, wherein "XX" represent 1-2, 2-3, and 3-4 upshifts, or 4-3, 3-2, or 2-1 downshifts. Figure 11 shows, schematically, the control logic that schedules locking and unlocking, i.e., application and release, of the torque converter bypass clutch 82 according to the present invention. The converter clutch control algorithm is entered at 188, and at 190 a check is made to determine whether the commanded gear is other than the first gear. If statement 190 is true, the vehicle speed at which the torque converter is locked VS LK and the vehicle speed at which the torque converter clutch is unlocked VS UNLK, are calculated at 192 thus VS LK = FN[GR CM]LS +(TQ INTR*FN[GR CM]LTQ) VS UNLK = FN[GR CM]US + (TQ INTR * FN[GR CM]UTQ) wherein FN[GR CM]LS is the vehicle speed corresponding to the current commanded gear at which the torque converter bypass clutch is locked according to the reference schedule of Figure 5; TQ INTR is the torque interpolation factor of Figure 6; and FN[GR CM]LTQ is the vehicle speed corresponding to the locked condition of the torque converter bypass clutch, determined by calibration and compensating for engine output torque reduction such that when it is multiplied by TQ INTR, and that product is added to the vehicle speed obtained from the schedule of Figure 4, an acceptable gear shift results. Figure 12 shows a function relating the variable FNXLTQ over the range of throttle position, which is stored in electronic memory, wherein X is a reference to the commanded gear ratio and L to the locked condition of clutch 82. A similar schedule of values for FNXUTQ is also stored in electronic memory and recalled as required from memory on the basis of the current operating throttle position. Statement 192 also calculates vehicle speed at which the torque converter bypass clutch 82 is unlocked VS UNLK = FN[GR CM]US +(TQ INTR*FN[GR CM]UTQ) wherein FN[GR CM]US is the vehicle speed value from the reference schedule of Figure 5 where a torque converter bypass clutch is scheduled to unlock; TQ INTR is the torque interpolation factor; and FN[GR CM]UTQ is the vehicle speed corresponding to the commanded gear ratio established by calibration that compensates for engine output torque reduction such that, when it is multiplied by TQ INTR and that product is added to vehicle speed from the reference schedule of Figure 5, an acceptable gear shift results. At statement 194, VSBART is compared to VS LK to determine whether current vehicle speed is greater than the torque compensated vehicle speed at which the torque converter clutch is to lock. If 194 is true, at 196, FLG CRV DS is set, thereby indicating the torque converter bypass clutch is to be locked. Control then passes to statement 202 where FLG CRV LK is set equal to 1.0 closing the output and driver circuit 66 to energise the converter bypass clutch solenoid 78 such that bypass clutch 82 is locked. If statement 194 is false, at 200, FLG CRV DS is set equal to zero, and at 202, FLG CRV LK is also set equal to zero. This alternative resetting of FLG CRV LK goes to the output driver circuit 66 to apply a signal to bypass clutch solenoid 78 so that bypass clutch 82 is unlocked.

Claims: A method for controlling gear ratio changes in a multiple gear ratio automatic transmission (11) for a motor vehicle having an engine (10) controlled by its throttle position by reference to a gear shift schedule defining conditions under which upshifts or downshifts in gear ratio from a current gear ratio can occur, characterised by the steps of: developing said gear shift schedule at reference engine output torque BTR BASE ; determining the current magnitude of reference engine output torque BTR BASE ; determining current engine output torque ; determining a vehicle speed adjustment to account for a difference between the current engine output torque and reference torque BTR BASE; and performing one or both of steps A and B, where step A comprises: determining from the gear shift schedule a predetermined vehicle speed FNXXS above which an upshift from the current gear ratio can occur; calculating engine torque compensated vehicle speed from said vehicle speed adjustment and said predetermined vehicle speed; comparing current vehicle speed to the engine torque compensated vehicle speed; and producing an upshift when said comparison indicates current vehicle speed exceeds said engine torque compensated vehicle speed; and step B comprises: determining from the gear shift schedule a predetermined vehicle speed FNXXS below which a downshift from the current gear ratio can occur; calculating engine torque compensated vehicle speed from said vehicle speed adjustment and said predetermined vehicle speed; comparing current vehicle speed to the engine torque compensated vehicle speed; and producing a downshift when said comparison indicates current vehicle speed is less than said engine torque compensated vehicle speed. A method as claimed in claim 1, wherein the step of determining engine torque compensated vehicle speed comprises: calculating normalised engine torque output TQ NORM defined as the ratio of TQ NET/BTR BASE; establishing a function relating torque interpolation factor TQ INTR and TQ NORM; determining the engine torque interpolation factor TQ INTR corresponding to current TQ NORM; determining vehicle speed adjustment FNXXTQ for an upshift or downshift from the current gear ratio corresponding to the current throttle position; and calculating the engine torque compensated vehicle speed from the relation FNXXS + (TQ INTR * FNXXTQ). A method as claimed in claim 1 or claim 2 in which said gear shift schedule includes provision for gear ratio changes to be made on the basis of engine speed, which also includes the steps of: determining an engine speed adjustment to account for a difference between the current engine output torque and said reference torque BTR BASE; determining from the gear shift schedule a predetermined engine speed NEXXS above which an upshift from the current gear ratio can occur; calculating engine torque compensated engine speed from said engine speed adjustment and said predetermined engine speed; comparing current engine speed to the engine torque compensated engine speed; and producing the upshift when said comparison indicates current engine speed exceeds said engine torque compensated engine speed. A method as claimed in claim 3, wherein the step of determining engine torque compensated engine speed comprises: calculating normalised engine torque output TQ NORM defined as the ratio of TQ NET/BTR BASE; establishing a function relating torque interpolation factor TQ INTR and TQ NORM; determining the engine torque interpolation factor TQ INTR corresponding to current TQ NORM; determining engine speed adjustment NEXXTQ for an upshift from the current gear ratio; and calculating the engine torque compensated engine speed from the relation NEXXS + (TQ INTR * NEXXTQ). A method as claimed in any preceding claim for use in a transmission (11) having a torque converter (84) controlled by a bypass clutch (82), the method further comprising the steps of: determining the current commanded gear ratio GR CM; developing a bypass clutch schedule at reference engine output torque BTR BASE, the schedule defining conditions under which the bypass clutch is locked; determining a bypass clutch vehicle speed adjustment to account for a difference between the current engine output torque and reference torque BTR BASE; determining from the bypass clutch schedule a predetermined bypass clutch lock vehicle speed FN[GR CM]LS above which the bypass clutch can lock; calculating bypass clutch lock engine torque compensated vehicle speed from said bypass clutch vehicle speed adjustment and said predetermined bypass clutch lock vehicle speed; comparing current vehicle speed to the bypass clutch lock engine torque compensated vehicle speed; and locking the bypass clutch when said comparison indicates current vehicle speed exceeds said bypass clutch lock engine torque compensated vehicle speed. A method as claimed in any one of claims 1 to 4 for use with a transmission (11) having a torque converter (84) controlled by a bypass clutch (82), the method further comprising the steps of: determining the current commanded gear ratio GR CM; developing a bypass clutch schedule at reference engine output torque BTR BASE, the schedule defining conditions under which the bypass clutch is unlocked; determining a bypass clutch vehicle speed adjustment to account for a difference between the current engine output torque and reference torque BTR BASE; determining from the bypass clutch schedule a predetermined bypass clutch unlock vehicle speed FN[GR CM]US below which the bypass clutch can unlock; calculating bypass clutch unlock engine torque compensated vehicle speed from said bypass clutch vehicle speed adjustment and said predetermined bypass clutch unlock vehicle speed; comparing current vehicle speed to the bypass clutch unlock engine torque compensated vehicle speed; and unlocking the bypass clutch when said comparison indicates current vehicle speed is less than said bypass clutch unlock engine torque compensated vehicle speed. A method as claimed in claim 5, wherein the step of determining bypass clutch lock engine torque compensated vehicle speed comprises: calculating normalised engine torque output TQ NORM defined as the ratio of TQ NET/BTR BASE; establishing a function relating torque interpolation factor TQ INTR and TQ NORM; determining the engine torque interpolation factor corresponding to current TQ NORM; determining bypass clutch lock vehicle speed adjustment FN[GR CM]LTQ corresponding to the current throttle position; and calculating the bypass clutch lock engine torque compensated vehicle speed from the relation FN[GR CM]LS + (TQ INTR * FN[GR CM]LTQ). A method as claimed in claim 6, wherein the step of determining bypass clutch unlock engine torque compensated vehicle speed comprises: calculating normalised engine torque output TQ NORM defined as the ratio of TQ NET/BTR BASE; establishing a function relating torque interpolation factor TQ INTR and TQ NORM; determining the engine torque interpolation factor corresponding to current TQ NORM; determining bypass clutch unlock vehicle speed adjustment FN[GR CM]UTQ corresponding to the current throttle position; and calculating the bypass clutch unlock engine torque compensated vehicle speed from the relation FN[GR CM]US + (TQ INTR * FN[GR CM]UTQ). A method as claimed in claim 1 in which the control is effected with the aid of a digital computer, characterised by the steps of: providing said computer with a data base including at least said gear shift schedule at reference engine output torque BTR BASE, the schedule defining conditions under which upshifts in gear ratio from a current gear ratio can occur, current magnitudes of reference engine output torque BTR BASE, and a vehicle speed adjustment to account for a difference between the current engine output torque and said reference torque BTR BASE; repetitively calculating in the computer current engine output torque TQ NET; repetitively determining in the computer the current magnitude of reference engine output torque BTR BASE; repetitively determining from the gear shift schedule a predetermined vehicle speed FNXXS above which an upshift from the current gear ratio can occur; repetitively calculating in the computer engine torque compensated vehicle speed from said vehicle speed adjustment and said predetermined vehicle speed; repetitively comparing in the computer current vehicle speed to the engine torque compensated vehicle speed; and producing an upshift when said comparison indicates current vehicle speed exceeds said engine torque compensated vehicle speed. A method as claimed in claim 3 in which the control is effected with the aid of a digital computer, characterised by the steps of: providing said computer with a data base including at least said gear shift schedule at reference engine output torque BTR BASE, the schedule defining conditions under which upshifts in gear ratio from a current gear ratio can occur, current magnitudes of reference engine output torque BTR BASE, and an engine speed adjustment to account for a difference between the current engine output torque and said reference torque BTR BASE; repetitively calculating in the computer current engine output torque TQ NET; repetitively determining in the computer the current magnitude of reference engine output torque BTR BASE; repetitively determining from the gear shift schedule a predetermined engine speed NEXXS above which an upshift from the current gear ratio can occur; repetitively calculating in the computer engine torque compensated engine speed from said engine speed adjustment NEXXTQ and said predetermined engine speed; repetitively comparing in the computer current engine speed to the engine torque compensated engine speed; and producing an upshift when said comparison indicates current engine speed exceeds said engine torque compensated engine speed. A system for controlling gear ratio changes in an automatic transmission (11) for use in a motor vehicle by reference to a gear shift schedule defining conditions under which upshifts or downshifts in gear ratio from a current gear can occur, comprising: an engine (10) having a variable position throttle for controlling the engine; means containing said gear shift schedule developed at reference engine output torque BTR BASE and means for determining the current magnitude of reference engine output torque BTR BASE; means for calculating current engine output torque TQ NET; means for determining current vehicle speed; means for determining a vehicle speed adjustment to account for a difference between the current engine output torque and reference torque BTR BASE; means for determining from the gear shift schedule a predetermined vehicle speed FNXXS above which an upshift or downshift from the current gear ratio can occur; means for calculating a respective engine torque compensated vehicle speed for an upshift or downshift from said vehicle speed adjustment and said respective predetermined vehicle speed; means for comparing current vehicle speed to the engine torque compensated vehicle speed; and means for producing an upshift or downshift when said comparison indicates current vehicle speed respectively exceeds or is less than said respective engine torque compensated vehicle speed. A system as claimed in claim 11 which also includes: means for determining current engine speed; means for determining an engine speed adjustment to account for a difference between the current engine output torque and reference torque BTR BASE; means for determining from the gear shift schedule a predetermined engine speed NEXXS above which an upshift from the current gear ratio can occur; means for calculating engine torque compensated engine speed from said engine speed adjustment and said predetermined engine speed; means for comparing current engine speed to the engine torque compensated engine speed; and means for producing an upshift when said comparison indicates current engine speed exceeds said engine torque compensated engine speed. A system as claimed in claim 11 or claim 12, wherein the transmission (11) has a torque converter (84) controlled by a bypass clutch (82), the system further comprising: means for determining the current commanded gear ratio GR CM; means containing a bypass clutch schedule developed at reference engine output torque BTR BASE, the schedule defining conditions under which the bypass clutch is locked, and a bypass clutch vehicle speed adjustment to account for a difference between the current engine output torque and reference torque BTR BASE; means for determining from the bypass clutch schedule a predetermined bypass clutch lock vehicle speed FN[GR CM]LS above which the bypass clutch can lock; means for calculating bypass lock engine torque compensated vehicle speed from said bypass clutch vehicle speed adjustment and said predetermined bypass clutch lock vehicle speed; means for comparing current vehicle speed to the bypass clutch lock engine torque compensated vehicle speed, and means for locking the bypass clutch (82) when said comparison indicates current vehicle speed exceeds said bypass clutch lock engine torque compensated vehicle speed. A system as claimed in claim 11 or claim 12, wherein the transmission (11) has a torque converter (84) controlled by a bypass clutch (82), the system further comprising: means for determining the current commanded gear ratio GR CM; means containing a bypass clutch schedule developed at reference engine output torque BTR BASE, the schedule defining conditions under which the bypass clutch is unlocked, and a bypass clutch vehicle speed adjustment to account for a difference between the current engine output torque and reference torque BTR BASE; means for determining from the bypass clutch schedule a predetermined bypass clutch unlock vehicle speed FN[GR CM]US below which the bypass clutch can unlock; means for calculating bypass clutch unlock engine torque compensated vehicle speed from said bypass clutch vehicle speed adjustment and said predetermined bypass clutch unlock vehicle speed; means for comparing current vehicle speed to the bypass clutch unlock engine torque compensated vehicle speed, and means for unlocking the bypass clutch (82) when said comparison indicates current vehicle speed is less than said bypass clutch unlock engine torque compensated vehicle speed.

Inventors: GREENE THOMAS L, PALANSKY BRUCE J, SCHOCK EILEEN ANN, GREENE, THOMAS L., PALANSKY, BRUCE J., SCHOCK, EILEEN ANN
Applicants: FORD FRANCE, FORD MOTOR CO, FORD WERKE AG, FORD FRANCE S. A., FORD MOTOR COMPANY LIMITED, FORD-WERKE AKTIENGESELLSCHAFT
Application year: 1994
Main classification: F16H61
IPC codes: F16H61